Fluid operated device



v. 27, v E942.

E. W. MCKINNEY FLUID OPERATED DEVICE Filed Jan. 29, 1940 S1:

Patented Jan. 27, 1942 FLUID QPERATED DEVICE Elslnere `\/V.'lVIcKinlney, Cleveland, Ghio, assignor to The McKinney Tool and Manufacturing Company Application January 29, 1940, Serial No. 316,177

My invention relates to uid operated device for accelerating or moving a mass in substantial .accordance with another mass.

An object `of vmy .invention is to prox/idea device to accelerate a first mass from a rstvelocity to .a velocity governedby the y velocity of a second mass.

Another object of. my .invention is to provide a device to accelerate Aa .mass from -agvelocity of zero to a velocity governed by .thevelocity -of a second vmass and to cause the velocity ofthe first mass to substantially equal the velocity of the second mass.

Still -another object of my invention is v,to provide an acceleration device which will cause va stationary mass to acceleratetofa speed governed by the speed of a moving mass and cause the accelerated mass to -follow .thespeed variations in said moving mass.

A further-.object .of .my inventionis to provide adevice for paralleling velocity.

Another objectof Ymy invention is to provide a device which will cause a `relatively .large mass to accelerate to a Xed velocity ina relativelyshort distance and to relieve the deviceoisubstantially all yof the strain due vto theforce Anecessary to produce the acceleration.

Still another lobject .of .my invention yis to provide .a device which 'will actuate a rst mass to a speed governed by the speed .ofa second` mass and which will cause .therst-mass `to follow any variations in speedwhich may be :evidenced by the second mass.

Another object of myinvention is toprcvideev device which will laccelerate a first mass-from lli) Zero velocity to the velocity of a second massand f which will regulate the 3iirt mass rto .parallel the velocity of the second mass after `the .acceleration periodis over and which will .cause thev rst mass to accelerate from the regulated velocity back to Zero velocity after therst .mass has lpassed through Ya certain distance.

A further object of .my invention Vis to provide .a system lfor cutting off moving bar-stock in which the bar-stock -is moving at a variable (Cl. 2li-69) locity of the movingbar-stock to zero afterthe bar-stock is cut Off.

A further object of myinvention is .'to'gprovide an acceleration device whichwill rapidly acceleratea relatively. large mass with a minimum .of shock.

Another object of my invention isto 'provide a device having van urging force .associated therewith which is held in balancebya'iiuid Iforce and to overthrow .the established balance lin response to the difference between twovelocities and thereby cause one of the velocities to be affected (by the unbalancedpurging force).

Still another object of .my invention is to'furnish. a velocity changing device which responds to two velocities .and which changes one )of the velocities to which it responds.

.Another object of my invention isto 'provide `a system for cutting oi :moving 'bar-stock in .which the bar-stock .is continuously .driven at a substantiallyv constant speed and infwhich the cut-*or machine operates in a Cycle; one round .of the cyclebeing to ,accelerate the cut-oil. mechanism from zero velocity to the velocity ofthe .moving bar-stock, to cut through the' bar-stock while the rbar-stock and the cut-01T machine are traveling at substantially equal velocitiesytoaccelerate the cut-01T ymachine back toits initial zero velocity and to reset the acceleration'device to prepare it for another cycle. Y

A further object of. my invention isv to.provide a device for rapid acceleration of .fa `relatively large mass and to reduce the shocker jarzoccasionedby the rapid acceleration.'

Figure 1 isa sectional vievzfcf part of :my in'- vention with portions `broken away and showing the actuating cylinder.

` Figure 2 is a sectional View of another part .of my invention with portions broken away and including a diagrammatic sketch showing rone manner in which my..invention can .be used. Figure 2 is adapted tobeplaced at 'the rightend of Figure 1 to form an integral device.

With reference to the drawing my ,invention comprises adevice vto .regulate the acceleration and the velocity of a body or mass bythe velocity of another body .or mass. Figure 2 shows my invention as applied to an automatic machine for cutting off moving bar-stock. Itis .to be understood however, that my invention may be applied to many other .acceleration problems and that .I am not to be limited to cut-ofi machnes as the illustration of the cut-oli; machine is merely'to aid in the description.

My invention comprises a stationary actuating the velocity of the moving bar stock I6.

housing indicated generally by the reference character I0. The actuating housing is preferably cylindrical and is attached to a stationary hollow collar II by means of an attaching ilange 6. At the endl of the housing I and adjacent the hollow collar I I I provide a ud seal 9 which provides an opening into the stationary housing I0 for a movable piston connecting rod 28 and for retaining a fluid with which the housing is substantally lled. .At the other end of the housing I0 I provide a fluid seal 8 and a closing plate 1 for retaining the iluid with which the housing is substantially nlled. The piston connecting rod 28 is adapted to move freely within the hollow portion of the collar II and is attached through a universal joint 26 to a mass attaching plate I3 which is in turn attached to a mass which is to be accelerated by my invention. For purposes of description I show a saw I4 and a saw actuating motor I5 which also constitute a mass attached to the mass attaching plate I3 and adapted to be accelerated by my invention.

A length of bar stock I6 is moving continuously and my invention is designed to accelerate the saw I4 and the saw actuating motor I5 from zero velocity to a velocity substantially equal to Upon the velocity of the saw I4 and the saw actuating motor I5 substantially equalling the velocity of the moving bar stock I5 my device is designed to cause the accelerated mass I4 and I5 to stop accelerating and to parallel the velocity of the ymoving bar stock I5 while the saw I4 cuts through the b-ar stock I5. After the bar stock I6 has been severed my device is designed to accelerate negatively the moving mass I4 and I5 back to zero velocity without a jarring shock.

Throughout this description I shall use the word acceleration to include both positive and negative change in velocity. That is to say I Ashall use the technical meaning of the word acceleration which includes the popular meanings of the words acceleration and deceleration Where it is necessary to differentiate between the popular conception of acceleration and "deceleration I shall use positive acceleration engagement of the flag by the moving barstock causes the flag carriage I1 to slide along the flag carriage track I8 at` the samevvelocity as the bar-stock I6 is moving and exercise a pulling force on a length of drill rod 2l having square section. The drill rod 2| which may be of adjustable length to allow for dilerent size pieces of bar-stock is attached to the flag carriage I1 in a manner which permits free rotation with respect to the flag carriage I1 but prevents horizontal sliding with respect to it.

The pulling movement which is exercised on the drill rod 2l is translated into rotational motion by means of a geared rack 22 meshing with one end of a pinion 23. The rotational movement of the pinion 23 is retranslated into a longitudinal pull by means of the other end of the pinion 23 meshing with a geared rack 24 which is integral with a valve control rod 25. By means of the geared connections between the valve control rocl 25 and the flag carriage I1 it is to be seen that a movement of the :dag carriage I1 under the influence of the moving bar-stock is translated in a :Fixed proportion to cause a movement of the valve control rod 25.

The valve control rod 25 passes through a universal joint 25 which allows for slight misalignments in various connected parts of my device and through the hollow collar connection I I and into the hollow piston connecting rod 28 in the stationary actuating housing IIl. The universal joint 26 attaches the movable piston connecting rod 28 to the mass I4 and I5 which is to be accelerated. A spring 3I is positioned to bias the mass I4 and I5 and is adapted to exert the accelerating force against the mass I4 and I5 and moves same when the fluid in the actuating device permits it. It is to be understood that any force producing means may be used in the place of the spring 3I.

The stationary actuating housing I0 into which the movable valve control rod 25 passes and from .Y which the piston connecting rod 28 is controlled to permit actuation of the mass I4 and I5 by the spring 3I is comprised of a stationary cylinder 32 and a movable piston 33. The movable piston 33 divides the actuating housing I 0 into two compartments 29 and 30 and provides a fluid seal between them. The piston 33 is connected to the piston connecting rod 28 and has a skirt 34 with ports 35 through it. There is also a port 36 through the piston head. The ports 35 and 36 permit the passage of fluid through the movable piston 33. The fluid which the actuating housing IIJ contains is preferably oil, however, any suitable fluid may be used.

Inside the movable piston 33 there is a piston sleeve 31 which is movable with respect to the movable piston 33. The piston sleeve 31 is placed closely adjacent the piston skirt 34 and contains ports 38 which are adapted to register with the ports in the piston skirt. Ports 4I are also provided to permit passage of the fluid through the piston sleeve head. As the piston sleeve 31 is movable with respect to the piston 33 I have provided a widened circumferential groove 39 which assures that the iluid will be able to pass from one compartment to the 'other when the piston sleeve 31 is at the extreme ends of its travel with respect to the piston 33.

Connected to the valve control rod 25 which extends to the geared rack 24 and which is movable in response to the movement of the flag carriage I1 is a valve ring 4U which is slidable to regulate the size of the opening of the ports 38. The valve ring 40 is connected to the valve control rod 25 by means of a taper pin 41 and adapted to move with respect to the piston sleeve 31 to regulate the flow of the iluid from one compartment to the other through the piston `sleeve ports 38. The regulatory movement of the ring 40 is derived from the movement of the barstock I5 by way of the flag carriage I1, the drill rod 2I, the rack and pinion connections and the valve control rod 25.

Assuming that the saw I4 and the saw actuating motor I5 are standing at zero velocity and a motor is driving the bar stock I5 toward the right by means of rollers 45 the action which takes place in my device is as follows: The barstock I5 engages the flag 20 and pushes the nag-carriage I1 along the track I8 at the same Velocity that the bar-stock I6 is being driven.

The .suddenmovement -o :the iag .carriage II causes Va longitudnal. movement :of the .length of Ydrill-:rod 2I 'and the movementis transferred to the valve ycontrol rojcl .25 by means Aof the `rack 22, the pinion 23 and the rack 24. Movement of the valve control ro`d 25 causes the port regulating ring 40 to move to the right and open the port 33. .Due to luid'pressure in compartment 30 the fluid flows through the opened portf38 4into the compartment 29 which is at allesser` pressure. The pressure which causes the flow oi the iiuid is derived fromthe force of the :spring v3| biasing the mass attaching plate I3 tothe right. As the mass yattaching plate' is attached to the piston 33 by means .of the `hollow piston connecting rod 28 the force of the .spring'3l is opposed or taken up or balanced by the' fluid pressure in the compartment'3 pushing .against 'the piston '33. The stronger the spring 3l the greater the fluid pressure in compartment T33 las thefluidv pressure is `cause'dby the force of the spring 3i. As the fluid flows through the open port Y38 the lpressure in the compartment `30-is reduced and the force of the spring 3i being no longer balanced by the substantially equal and opposite force of vtheiluid in thecompartment 3i! accelerates in a positive manner the saw i3 and the saw actuating motor l-'to vthe right. As the accelerated'mass Il! and I5 is attached'to the plate I3 which in turn is attached to the piston connecting rod 23, the connecting rod 28 and the piston '33 to Which lthe connecting rod' 28 isconnected are positively accelerated to the right also. The positive acceleration offthetrnass I3 and I3 and the operatingr parts I3, '23 and 33 will co-ntinue until the fluid pressure in compartment 33 equals the force exerted by the spring 3i. This equalization of forces will not be reached until the ports 33 are substantially closed. However, the ports 38 will remain open vuntil the spring 3I has accelerated the mass I4 and I5 up to the velocity at which the bar-stockv i6, the ilag carriage Il', the pinion 23 the racks (22 and 24 and the valve control rod 25 are moving.

When the equalization of velocities has been reached a balance will be brought about between the force of the spring 3l and the back force of the uid in the chamber 33 and the port 38 will be substantially closed to prevent further acceleration. However the port 38 will remain open M and I5. If spring 3i pushes the mass I4 and I5 too fast the openport in the moving piston sleeve 3'! will overtake or catch up to the moving port regulating ring 43 and the port opena `threeaquarter of ancinchtravel vby .the facceb .eratedv mass I4. andIS .willsresult in; substantial equality ofvlocitiesbetweenrthe mass I4 :and I5 and the moving bar-stock I6. I have :also designedmy .device Ysotthat a travel of approximately :26 inches, for example, by the :saw and Yby thebar-:stock while the'saw. I4 sI :cutting the Shar-stock I6 will 'permit fthe .severance :of the-bar I6. I :also provide aiperiod of negative acceleration. l.During this period r`the moving parts of my device may travel, for example, three-.quar-tersof an inch and then` the "velocity Yof' the Amoving'part is reduced to zero'in thei'ollowing manner: 'When saw' I4 lcuts oil the rlength :of the bare-stock` I6 the .flag carriage I'I will ^no longer be .pushed along 'by the'movement o'frthe bar-stock yas the severed portion will drop away vfrom .contact wi'ththe iiag 20 yand the .carriage will stop ydue to frictional resistance on vthe track E58. If' rapid negative acceleration is desired the carriage can be brought to an `abrupt stop-by means of an .adjustable bumper Yor by increased frictional resistancebetween the flag carriage II and the `track I3. The frictional resistancefcould be governed by any of the known methods.

'The slightest negativev acceleration'of the iiag carriage I"I- causes a rotational movement ofthe Y pinion`23 and a longitudinal thrust on the 'valve ing will be throttled down preventing the uid from iiowing out of chamber '33 as rapidly and thereby increasing the force of the pressure in chamber 3D to a point Where it will balance the force of the spring 3| and slow the mass down. On the other hand if the velocity of the saw It and the motor I5 tends to fall below the velocity f of the moving bar-stock I3 the valve control rod will move faster than the port 33 and open the port wider thereby increasing the fluid flow therethrough and further decreasing the fluid pressure Which is restraining the spring 3i The greater reduction in the back force against spring 3I w11 cause the spring 3l to accelerate the mass Ill and I5 and increase the velocity of the mass IA and I5. 'In my device I'fhave designed the yinitial acceleration period so that, yfor example,

3l' -with respect to 'the piston 33.

control rod 25. The thrust on the valve control rod causes a negative acceleration of the port regulating r-ing 40 and the port A38 Iwhich is stilllbeing urged by the spring-'3l overtakes the ring "42| vand the 'opening from chamber 33 into chamberr29 is closed. Theslight forward vmovement which the mass I4 and"l'5"takes aftertheclosing of the port 38 compresses the fluid in chamber 30 to the point when the forcevit exerts equalsthe force ofthe spring `3I and all movi-ng parts including the ymass I4 and I5 brought to a stop.

The piston sleeve 3'I is -slidably positioned adjacent the skirt of piston 33 to provide for absorbing shock during the initial positiveacc'eleration period. 'In cases Where the absorption of shock' is unnecessaryr the piston sleeve '31 is not exactly essential to the operation of the device and asmall portV such as port 38 through the piston lskirt 34 with the port regulating ring 40 positioned to Aopen and close it would sufce. Ordinarily smooth shockless acceleration of the mass I4 and I5 is desirable. 'I have therefore provided the shock absorbing piston sleeve '3l and a gear Aand lever means indicated generally by the reference character for causing relative motion between 'the piston -"-33 and -the sleeve 3'.' whenv the 4spring 3| actuates themass 'I4 and I5 and the pistonI 33.

The relative motion gear and lever means 59 is mounted in the left-handend ofthe deviceand comprises `a carrier plate l5I extending outwardly vfrom the head ofthe piston 33 and adapted to carry the gears which aetuate the 'piston sleeve The carrier plate =5I ispreferably integral with theheadl of the piston 33 but separate pieces may be kused if suitable attaching means are providedto connect them together. A bell crank -52 is pivoted to the carrier-plate 5i. The end 53 of the bell crank 52 is slidably lconnected to the stationary-actuating housing I3 by meansr of the end 53being positioned in a curved slideway-54 inthe underneath side of the stationary housing I0. A longitudinal movementof the piston 33 vand theA carrier plate 5I 'will cause the end '53 of the bell 'crank '52 to slide in the curved V'slideway'54 thereby turning the 'bell crank about its pivot point lat52. The y other end of the bell crank 52 is pivotally connected toa connecting link 55 at point 56. An end 51 of the connecting link 55 is slidably connected in a cam slot 58 in the movable carrier plate 5I. It will be seen therefore, that a movement of the piston 33 with respect to the stationary housing I will cause a rotational movement of the bell crank 52 and an enlarged rotational movement of the connecting link 55. An end 53 of the connecting link 55 is pivotally connected to one end of a second connecting link 66. The other end of the second connecting link 66 is attached to a crank gear 6I which is pivotally connected to the carrier plate I at point 62. The teeth of the crank gear 6I mesh with a rack 65 which is integral with the piston sleeve 31. The enlarged rotational movement of the connecting link 55 therefore causes a longitudinal movement of the piston sleeve 31. The longitudinal movement of the piston sleeve 31 is greater than the longitudinal movement of the piston 33. Due to the increased longitudinal movement of the piston sleeve 31 the port 38 does not drop far enough behind the port regulating ring 46 during a positive accelerating period to eilect a too sudden opening of the port 38 and a jar during acceleration. In other words, when the port regulating ring 46 is moved longitudinally to the right by the bar-stock I6 and the port 38 is opened to permit fluid flow and thereby cause a movement of the piston 33, the piston sleeve 31 moves at a greater distance to the right toward the ring 46 than does the piston 33 and prevents a too sudden opening of the port 38. The movement of the port regulating ring 46 to the right when the piston 33 and the carrier plate are returned to their original position with respect to the stationary housing Ill. As the end or pin 53 re-enters the curved slideWay 54 and continues to slide back, a port regulation is obtained to prevent jar during the negative acceleration f period.

I provide my acceleration device With another means for reducing shock due to rapid acceleration. It is a suction means and is indicated generally by the reference character 66. The suction means 66 is comprised of a cylinder 61 integral with the head of the piston sleeve 3'I.` A suction piston 63 is provided on the end of the valve control rod and is adapted to fit inside the cylinder 61 and to be actuated with respect to the cylinder 61 by the movements of the valve control rod 25. A longitudinal movement of the valve control rod 25 to open the port 38 will cause a longitudinal movement of the suction piston 68 with respect to the suction cylinder 61 in the head of the piston sleeve 31. The relative movement of the suction piston 68 with respect to the suction cylinder 61 creates a partial vacuum in the suction cylinder 61 and pulls the entire piston sleeve 31 to the right in Figure l with respect to the valve control rod 25. The movement of the piston sleeve 31 to the right with respect to the valve control rod 25 preventsK a sudden opening of the port 38 and the accompanying shock due to too rapid acceleration of the mass I4 and I5.

The port 38 is partially opened by the movement of the valve control rod 25 before the partial vacuum in the suction cylinder 61 is sufcient to draw the piston sleeve 31 toward the valve control rod 25. The partial opening of the port 38 allows a fluid flow from chamber 30 into chamber 29 and causes an acceleration of the piston 33, the piston sleeve 31, the valve control rod 25 and the mass I4 and I5. The suction piston 68 is provided with a ball-check valve 69 and a passageway 16 from inside the suction cylinder 61 to the chamber 29. The ball-check valve 69 is adapted to permit removal of any fluid which enters the suction cylinder 61 due to the partial vacuum which is created therein by a positive acceleration of the device. Should oil or fluid enter the suction cylinder 61, it is vented by the return of the port regulating ring 40 and the valve control rod 25 to a position which closes the port 38. The return of the valve control rod 25 to the closing position thrusts the suction piston 68 into the suction cylinder 61 and creates a iluid pressure therein which opens the ball-check valve 69 and allows the fluid to pass through the passageway 10 into the chamber 29.

Although I have illustrated my device as having two means of reducing initial accelerating shock it is to be understood that my device may be operative without either in those cases Where the shock is not damaging. 4It is also to be understood that the gear and lever means 56 for modifying movement between thepiston 33 and the piston sleeve 31 may be used without the suction means 66 and that the suction means 66 may be used without the gear and lever means 5D.

The suction means 66 when used in cooperation with the gear and lever means is a booster to accelerate the movement of the gear and lever means. Although the gear and lever means is designed to never get on dead center it may approach it enough to be sluggish. The use of the suction means 66 will reduce the amount of sluggishness.

My device is designed to operate automatically and a complete cycle of operation may be as follows: The moving bar-stock I6 which is driven through rollers 46 by the motor 45 engages the flag 20 of the movable flag carriage I1 thereby rotating the flag 26 about a pivot point 16 and causing an actuating arm 11 to engage a projection 18 on a turnable shaft 19, and turn the shaft. The turning of shaft 19 actuates a drill rod rotating arm 86. The actuation of the drill rod rotating arm 88 rotates the drill rod 2 I, which is connected to the rack 22 by a swivel joint 84, and operates a cam 8I. The operation of cam 8I controls a gear box 82 which is driven through the power line 85 by motor 45, to apply power through line 86 to drive the saw I4 forward on a pair of tracks 15. The saw I4 moves forward toward the bar-stock I6 and is positioned with respect to-the bar-stock I6 so that operation of the saw I4 by motor I5 cuts through the bar-stock. During the short interval of time necessary to position the saw I4 to cut the bar-stock I6 the positive acceleration of the saw I4 and the motor I5 to a velocity governed by the velocity of the moving bar-stock I6 has taken place. The terminal velocity of the saw I4 and its carrying mechanism is governed by the moving bar-stock I6 pushing the flag carriage I1 along the track I8 and is the same velocity that the bar-stock I6 is moving. The detailed operation of the acceleration mechanism and the means for paralleling the velocity of the mass I4 `and I5 with the velocity ofthe-moving bar stock I6- has heretoforebeenl described. After the saw I4 has cut through the bar-stock It which takes place during the periodv in which their velocities are substantially equal, thev severed end of the bar-stock |5dropsaway from Contact with the flag 20. As there Vis no longer a force against theA iiagv 20 it pivotsback to its initial position and the carriage stops. The return of thev flag 20 to its initiall position actuates cam 8| thereby influencing the gear box 82 to withdraw thev saw I4 from the bar-stock. During the nal withdrawal of the saw I4 a bell crank 81 is actuated which in turn operatesthe gear box 82 and its operation' causes power from the motor 45, which is still' actua-ting'thel barstock I Ii, to be applied te the massA attachingplatel I3 through line 88 to restore the accelerating device-to itsinitial position; that isto compress the spring 3| and prepare the device yfor anotherv operative cycle. During the period' in which the saw"|4 is withdrawn from the bar-stock Ithe saw I4' and the motor I5 are passing through their'perlod of negative" acceleration andbrought to zero velocity. The equipment is designed so that themoving parts reach zero velocity 'before actuating the bell crank 81 and before the moving bar-stock I6' engages the flag 20 to start anothery It is to be understood thati'my operative cycle. acceleration mechanism may be returned to its starting position by any means. crank or motor independent of thebar-stock drive could be used to reset spring 3| for another acceleration of mass I4' and I5.

As the operation of my device dependsupon the balance of pressurebetween compartment 2 9 and the spring 3| on one hand and the compartment 3|] on. the other hand', it will be seen that the movement of the piston connecting rod 28 with respect to the stationary cylinder 32 will change the volume andv therefore change the pressure balance within the cylinder 32 and thereby aifect the operation of my device. To compensate for the fluid displaced. by the piston connecting rod 23 I have designed the. fluid. seal i3 to float within the cylinder 32 andv establisha f third compartment 90 within the cylinder. Com-v partment 50 contains no fluid and .is ventedlto atmosphere through opening Si!y in the closing. plate 'I. A spring 92 is positioned between the closing plate IY and the fluid seal. 8 to bias the` fluid seal 8 ltoward the compartment 29; When my device is in an operative position. but does not have the force of the acceleratingispring'l on it the following conditions exist: Compartments 2S and 35' are substantially entirely lled with a fluid such as oil and there is no difference in fluid pressure between the compartments. 'I'he piston 33 which establishes a liquid iseal'between the compartments 29 and 30 is floating. That is,

it is not biased in any direction. When the force That is, a hand for fluid actuallypassing from one compartment ment 29funtil the fluid pressure in compartment 29 is substantially atmospheric.

When my device operates. to accelerate the mass I4.v and I5 thef piston connecting rod .28.

moves to the right a short: distance. and the fluid.

spaces inv compartments 2'9iandi 30l are. effectively increased .by part ofrodf 28 passing out of the cylinder Aby waylof the fluid seal 9'. This effective.

23 yfrom the cylinderA 32.v As both'- compartments- 25e-and illlare compensated forv the change'in pressure, there is no change inoney compartment with respect to the other dueto the movement of the` piston connecting rodL 28; Asbeforeex-l plained, thel acceleration of the mass I4 and I5l is causedv byy diierencesin fluid pressure between compartments 29 and 35 as regulated by fluid flow through the-port 38; It is thereforetobeseeny that the acceleration' ofthe massV I4 and I5 isnot affected by; the withdrawalwof the piston connecting red 28 from the cylinder 32 as theapparentl difference in fluid pressure which is created by the withdrawal is compensated for by a-movement'of the piston 33 and `by a movement of thefloating fluidfseal fwhich reestablishes and'k maintains a fluid pressure balanceY between the two compartments `29v and 30" except to the other; k

L summarizing, my device III is adapted' to'accelerate a mass I4 andv I5-from zerovelocityand limit itsspeed to theA velocity of av moving mass suchv as-thebar-stock Iandv tov cause the velocity of the accelerated massY I4 and I5 toparallel the velocity of the moving mass through'out'a xedv distance, that-is, thedistancerequired for'saw I4" piston sleeve 37Y andzthep'ort regulating ring 40" as they are all moving substantially at the same speed-*whicheis regulated' by the velocity ofthe moving mass I6; Further, my device Nis adapted to decelerate the moving mass I4' and' I 5" to change` their Velocity from that 'regulated by the bar-stock "I 6 to zero and automatically prepare itself for another' cycle.

While Iv have described my invention with a certain degree of particularity, it is understood that the present disclosure has been made only by'way of example and'that numerous changes in the details ofr construction and the combination and arrangement of vparts may be resorted to without departing from the spirit and scope of the invention as'hereinafter claimed..

I claim as my inventionv 1. Al device for accelerating a first massto a speed governed by the speed of a'fsecond mass comprising, in combination, energy means adapted to exert a force to accelerate said rst mass, hydraulic means for exerting a force to oppose the acceleration of said first mass, means actuated by said second mass for reducing the opposing force exerted by said hydraulic means thereby' causing said energy-means to accelerate saidfirst'mass, and val-ve meansregulated'by the the opposingforce exerted byf the'hydr'aulio means to cause said irst mass to maintain substantially the same speed as said second mass, said valve means comprising fluid orifice resisting means including a first orifice means movable with the rst mass and a second orice means movable with the second mass.

2. A device for accelerating a first mass to a speed governed by the speed of a second mass comprising, in combination, energy means adapted to exert a force against said rst mass, a iiuid reservoir for resisting the force exerted by said energy means, and valve means actuated by the relative speeds of said first and second masses for reducing the pressure in the said reservoir thereby causing the said energy means to accelerate said first mass to the speed of the second mass, said valve means comprising fluid orice resisting means including a rst orifice means movable with the rst mass [and a second orifice means movable with the second mass; y

for passing fluid from one chamber to the other and port opening and closing means actuated by said second mass for regulating said port opening to change the uid pressure in the high pressure chamber thereby causing the first mass to accelerate.

4. A device for equalizing the speeds of two masses comprising, in combination, a housing, movable piston means attached to one of said masses and positioned in said housing thereby dividing said housing into two chambers, force exerting energy means urging said piston in one direction, fluid means in one of said chambers for resisting said urging force, port means through said piston for passing said iiuid from one chamber to the other, and port covering means actuated by the other of said masses, said piston i 5. A device for equalizing motion between two masses comprising, in combination a fluid housing, piston means connected to the rst of said masses and dividing said fluid housing into two compartments, energy means adapted to exert an accelerating force against said piston means, fluid means in one 01 said compartments for exerting a resisting pressure against accelerating force, valve means in said housing for reducing said iiuid pressure to cause the said energy means to accelerate the said piston means and the said rst mass, said valve means being opened and closed in a fixed relation to the relative speeds of the said two masses.

6. A device for limiting and regulating the speed of an accelerating mass to the speed of a second mass comprising, in combination, a fluid housing, a piston connected to said accelerating mass and dividing said fluid housinginto two compartments, accelerating force means urging Cri said piston and said mass to accelerate, fluid means in one of said compartments compressed by and resisting said accelerating force, port means through said piston for relieving said fluid pressure to cause said accelerating force to exceed said resisting force thereby accelerating said piston and said accelerating mass and port opening and closing means actuated b-y and movable with said second mass for relieving said fluid pressure in accordance with the difference in speed between said second mass and said accelerating mass thereby causing said accelerating mass to attain a speed substantially equal to the speed of said second mass.

7. A device for regulating the acceleration and the speed of a rst mass by the speed of a second mass comprising, in combination, a fluid housing, a movable piston attached to said rst mass and dividing said fluid housing into two compartments and establishing a fluid seal therebetween,

accelerating force means urging said movable piston and said rst mass to accelerate, and said rst mass to accelerate, fluid means in one of said compartments resisting said accelerating ,force means, sleeve means adjacent said piston and movable relative thereto, port means in said piston and in said sleeve for relieving said fluid pressure to cause said accelerating force to exfor opening said port and relieving said iiuid pressure in accordance with the difference in speed between said second mass and said first mass and lever means connecting said sleeve to said piston whereby movement of the piston under the influence of the accelerating force will produce a proportional movement in said sleeve, the movement of the port means in said sleeve and the movement of the port regulating means adjusting the fluid flow through the pori; means to regulate the acceleration and speed of the rst mass by the speed of the second mass.

8. A speed equalizing device comprising, in combination, a fluid housing, a movable piston dividing said housing into two compartments and establishing a fluid seal therebetween, fluid means in one of said compartments, energy means for biasing said movable piston against tending to reduce said uid pressure in accordance with the speed of the port opening and closing means and causing said movable piston to move at a speed substantially equal to that of the port opening and closing means to maintain a relationship of opposing forces between the said energy means and the said fluid means.

9. A speed equalizing device comprising, in combination, a housing, movable piston means in said housing establishing two housing compartments with a liquid seal therebetween, a

liquid in one ofsaid compartments, means for urging said movable piston against said liquid to establish a liquid pressure against said piston which opposes the force of said urge, a port in said movable piston connecting said two ccmpartments 'and port closing means adapted to open said port in accordance with a certain speed which said movable piston is to equal, the opening of said port causing a reduction in liquid pressure and a movement of said piston and said port, the rate of movementI of said piston and said port being such as to close said port to reestablish a relationship between the force of the urging means and the force of the liquid pressure.

10. A device for regulating the acceleration and the speed of a rst mass by the speed of a second mass, comprising, in combination, a fluid housing, a movable piston attached to said iirst mass and dividing said fluid housing into two compartments and establishing a iiuid seal therebetween, acceleration force means urging said movable piston and said first mass to accelerate, fluid means in one of said compartments resisting said accelerating force means, sleeve means adjacent said piston and movable relative thereto, port means in said piston and in said sleeve for relieving said fluid pressure to cause said accelerating force to exceed said resisting force thereby accelerating said piston and said rst mass, port regulating means actuated by and movable with said second mass for opening said port and relieving said uid pressure in accordance with the difference in speed between said second mass and said first mass and vacuum means operable by said port regulating means for urging said sleeve means and said port means therein to move, the movement of the port means in said sleeve and the movement of the port regulating means adjusting the fluid ow through the port means to regulate the acceleration and speed of the first mass by the speed of the second mass.

11. A cut-off machine for paralleling movement of a saw with moving bar stock comprising, in combination, an actuating cylinder, a movable piston attached to said saw and dividing said actuating cylinder into tWo compartments, hydraulic means in one of said compartments, energy means urging said saw to accelerate and urging said movable piston against said hydraulic means to establish a pressure in said hydraulic means which is opposite to the pressure exerted by the energy means, movable port means through said movable piston for reducing said hydraulic pressure to cause said energy means to accelerate said piston and said saw, port opening and closing means for regulating the port opening through the said piston to regulate the oW of fluid from said cylinder compartment, said port opening and closing means being operatively connected to said moving bar stock and adapted to open and close said movable port in accordance with the diierence in speed between the bar stock and the saw, said piston moving faster than said port opening and closing means and closing said movable port when said saw is moving faster than said bar stock and said port opening and closing means moving faster than said piston and opening said movable port when said bar stock is moving faster than said saw.

12. A device for causing stationary saw means to accelerate to and parallel the speed of moving bar stock comprising, in combination, a cylinder having its axis parallel to the lines of travel of said bar stock and said saw means, a piston in said cylinder attached to said saw means and dividing said cylinder into two compartments, hydraulic means in said cylinder, said piston having skirt means extending in the direction of the comprising,

axis of said cylinder, said skirt means having port means therethrough for the passage of said hydraulic means from one compartment to the other, energy means for exerting a force against said stationary saw means and against said piston, said force compressing the hydraulic means in one of said compartments, port opening and closing means actuated by said moving bar stock and movable parallel to the axis of the said cylinder, said port opening and closing means being adapted to open said port When the bar stock is moving faster than said saw means to cause the energy means to accelerate the saw means and the said piston, until the saw means is traveling at the same rate of speed as the said bar stock, and said port being closed by the piston overtaking said port Iopening and closing means When said saw means is traveling at a rate of speed greater than said bar stock, the speed of the bar stock and the port opening and closing means and the speed of the saw means and the piston regulating the port opening to maintain a relationship between the force of the energy means and the hydraulic force to cause said saw means to parallel the speed of the bar stock While said saw means cuts through said bar stock.

13. A device for accelerating a iirst mass to a speed governed by the speed of a second mass comprising, in combination, energy means adapted to exert a force against said rst mass, a fluid reservoir with fluid therein for resisting the force exerted by said energy means, port means communicating with said fluid reservoir and actuated by the speed of one mass and port closing means movable relative to the port means and actuated by the speed of the other mass for regulating the opening of the port means in proportion to the relative speeds of said first and second masses thereby reducing the pressure of the fluid in said reservoir to cause the energy means to accelerate said first mass to substantially equal the speed of said second mass.

14. A device for accelerating a first mass to a speed governed by the speed of a second mass in combination, energy means adapted to exert a force against said first mass, a fluid reservoir With fluid therein for resisting the force exerted by said energy means, port means communicating with said fluid reservoir and actuated by the speed of one mass, port closing means actuated by the speed of the other mass for regulating the opening of the port means in proportion to the relative speeds of said rst and second masses thereby regulating the flow of the fluid in said reservoir to cause the energy means to accelerate said first mass to substantially equal the speed of said second mass, and means for modifying the movement of the port means with respect to the movement of the mass which aotuates said port means to provide a time v delay in the acceleration of said rst mass.

rst and second masses thereby regulating the pressure of the fluid in said reservoir to cause the energy means to accelerate said first mass to substantially equal' the speed of said second mass, and vacuum means for modifying the movement of the port means with respect to the movement of the mass Which actuates said port means to provide a time delay in the acceleration of said first mass.

16. A fluid device for accelerating a mass comprising, in combination, energy means adapted to exert an accelerating force against said mass, a housing having fiuid, piston means displacing fluid in said housing and adapted to receive the accelerating force of said energy means and govern the acceleration of said mass, the amount of said fluid displaced by said piston means varying as said piston means transmits accelerating force to said mass and means for compensating for the variation in the amount of fluid displaced by the said piston means.

17. A device for moving a first mass in accordance with the movement of a second mass comprising, in combination, means for moving the first mass, fluid regulating means for governing the moving means, and means responsive to the relative movements of the first and second masses for actuating the fiuid regulating means, said regulating means comprising fluid orifice resisting means including a first orifice means movable with the first mass and a second orifice means movable With the second mass.

18. A device for moving a first mass in accordance with the movement of a second mass comprising, in combination, means for moving the first mass, fluid regulating means for governing the moving means, said fluid regulating means comprising fiuid orifice resisting means having two orifice parts movable relative to each other, means responsive to the movements of the first mass for moving one of said parts, and means responsive to the movements of the second mass for moving said other part.

19. A device for moving a first mass in accordance with the movement of a second mass comprising, in combination, means for moving the first massy fiuid means opposing the movement of the moving means, iiuid regulating means for governing the fluid means, and means responsive to the relative movements of the first and second masses for actuating the fiuid regulating means, said regulating means comprising fluid orifice resisting means including a first orifice means movable With the first mass and a second orifice means movable with the second mass.

20. A device for moving a first mass in accordance with the movement of a second mass comprising, in combination, spring means for moving the first mass, fiuid means opposing the movement of the sprin-g means, fluid regulating means for governing the opposing means, and means responsive to the relative movements of the first and second masses for actuating the fluid regulating means, said regulating means comprising fiuid orifice resisting means including a first orifice means movable with the first mass and a second orifice means movable With the second mass.

21. A device for moving a first mass in accordance with the movement of a second mass comprising, in combination, spring means for moving the first mass, fluid means opposing the movement of the spring means, and fluid regulating means for governing the opposing means, and means responsive to the relative movements of the first and second masses for actuating the regulating means, said regulating means comprising uid orifice resisting means including a first orifice means movable with the first mass and a second orifice means movable -With the second mass, said first and second orifice means being movable relative to each other.

22. A device for moving a first mass in accordance with the movement of a second mass comprising, in combination, a fluid housing having a piston therein dividing the housing into two compartments, means for connecting thev first mass to the piston, means for moving thefirst mass and thus actuating the piston within the housing, fluid regulating means for governing the flow of fluid from one compartment to the other, upon the movement of the piston, said regulating means comprising a first means movable with the first mass and a second means movable with the second mass.

ELSMERE W. MCKINNEY. 

